Friction clutch control device driven by branch lubricating oil pressurization

Abstract

The invention discloses a friction clutch control device driven by branch lubricating oil pressurization, and relates to the field of marine transmission gear boxes and friction clutch control devices thereof. The problems that when a friction clutch control device of a traditional marine gearbox lubricating system supplies oil to a wet friction clutch, high-flow oil pumped out by a gearbox shaft oil pump passes through a pressure regulating valve and is changed into low pressure from high pressure, power loss is large, and the transmission efficiency of a gearbox becomes low are solved. Compared with a traditional friction clutch control device, the friction clutch control device is additionally provided with the working oil pump, the hydraulic motor, the first throttling valve and the working oil safety valve, the combination of the hydraulic motor and the working oil pump becomes a hydraulic element of a combined body capable of being pressurized, and only a small amount of low-pressure lubricating oil is used for being pressurized to become working oil; the rest of lubricating oil does not pass through the pressure regulating valve, power loss is reduced, and the transmission efficiency of the gearbox is improved. The method is mainly used for controlling the oil supply and drainage process of the friction clutch.

Description

Technical Field

[0001] The present invention relates to the field of marine transmission gearboxes and their friction clutch control devices. Background Art

[0002] The significant difference between a marine transmission gearbox and an industrial gearbox is that the marine transmission gearbox includes a marine gearbox lubrication system and a clutch, etc. Generally, its own gear shaft drives an oil pump to achieve self-circulation lubrication of the gearbox, rather than using an electric oil pump or an independent oil station for external oil supply. Therefore, the efficiency of the marine gearbox lubrication system including the shaft-driven oil pump becomes part of the transmission efficiency of the gearbox. Currently, the traditional marine gearbox lubrication system uses a large-flow shaft-driven oil pump to provide high-pressure oil (1.8 - 2.5 MPa) to supply working oil to the oil cylinder of the wet friction clutch. The control method of the friction clutch control device in its lubrication system is to reduce the high-pressure oil through a pressure regulating valve to provide low-pressure lubricating oil (0.1 - 0.5 Mpa) for gears, bearings, and wet friction clutches. After the oil cylinder of the wet friction clutch compresses the friction plate group, the required working oil volume is about 1% of the outflow of the shaft-driven oil pump. Therefore, a large amount of energy is lost when the large-flow high-pressure oil is reduced in pressure through the pressure regulating valve to become low-pressure oil, reducing the overall transmission efficiency of the marine gearbox. In addition, the energy lost due to pressure reduction becomes heat, increasing the temperature of the lubricating oil, and a large amount of cooling water required to cool the lubricating oil also increases additional energy consumption. Summary of the Invention

[0003] The purpose of the present invention is to solve the problem that when the friction clutch control device of the traditional marine gearbox lubrication system supplies oil to the wet friction clutch, the large-flow oil pumped out by the gearbox shaft-driven oil pump all passes through the pressure regulating valve and changes from high pressure to low pressure, resulting in large power loss and low transmission efficiency of the gearbox. A friction clutch control device driven by branch lubricating oil pressurization is provided.

[0004] The friction clutch control device driven by branch lubricating oil pressurization includes a shaft-driven oil pump, a safety valve, a relief valve, a pressure regulating valve, a switching solenoid valve, a quick oil filling solenoid valve, a one-way throttle valve, a quick release valve, and a pressure regulating valve; it also includes a working oil pump, a hydraulic motor, a first throttle valve, and a working oil safety valve;

[0005] The rotor shaft of the working oil pump is connected to the rotor shaft of the hydraulic motor through a coupling; the safety valve is arranged at the oil outlet of the shaft-driven oil pump to discharge the oil with overpressure in the oil circuit to the gearbox;

[0006] Moreover, the oil outlet of the shaft-driven oil pump is simultaneously connected to the oil inlet of the hydraulic motor and the oil inlet of the throttle valve. The oil outlet of the hydraulic motor is simultaneously connected to the low-pressure oil outlet of the pressure regulating valve, the oil inlet of the working oil pump, the oil outlet of the first throttle valve, and the oil inlet of the quick filling solenoid valve. The oil outlet of the first throttle valve is used as the oil outlet Pu of the control device, and this oil outlet Pu is used to supply lubricating oil to the gears in the gearbox and the bearings of the friction clutch in the gearbox.

[0007] The overflow valve is arranged at the oil outlet of the first throttle valve and is used to discharge the oil with excessive pressure in its corresponding oil circuit into the gearbox.

[0008] The working oil safety valve is arranged at the oil outlet of the working oil pump and is used to discharge the oil with excessive pressure in its corresponding oil circuit into the gearbox.

[0009] The oil outlet of the working oil pump is connected to the high-pressure oil inlet of the pressure regulating valve. And on the pipeline between the oil outlet of the working oil pump and the oil inlet of the quick discharge valve, a switching solenoid valve and a one-way throttle valve are successively arranged. The control port C of the pressure regulating valve is connected to the pipeline between the switching solenoid valve and the one-way throttle valve.

[0010] The oil outlet of the quick filling solenoid valve is connected to the pipeline between the quick discharge valve and the one-way throttle valve. The oil outlet Pw of the quick discharge valve is connected to the oil cylinder of the friction clutch in the gearbox.

[0011] Preferably,

[0012] The oil inlet, oil outlet, and oil drain port of the hydraulic motor all adopt a pipe joint structure.

[0013] The oil inlet and oil outlet of the working oil pump adopt a pipe joint structure.

[0014] Moreover, after the housing of the working oil pump and the housing of the hydraulic motor are coaxially and rigidly connected through a connecting plate, a combined hydraulic component is formed.

[0015] Preferably, the switching solenoid valve is a two-position three-way solenoid valve.

[0016] When the electromagnetic coil of the switching solenoid valve is energized, the oil outlet of the switching solenoid valve is connected to its oil inlet. At this time, the oil cylinder of the friction clutch in the gearbox is in the oil supply state.

[0017] When the electromagnetic coil of the switching solenoid valve is de-energized, the oil outlet of the switching solenoid valve is connected to its oil drain port. At this time, the oil cylinder of the friction clutch in the gearbox is in the oil drain state.

[0018] Preferably, the quick filling solenoid valve is a two-position two-way solenoid valve.

[0019] When the electromagnetic coil of the quick filling solenoid valve is energized, the oil outlet and the oil inlet of the quick filling solenoid valve are connected.

[0020] When the electromagnetic coil of the quick oil filling solenoid valve is de-energized, the oil outlet and the oil inlet of the quick oil filling solenoid valve are not connected.

[0021] Preferably, the flow diameter of the pressure regulating valve is only positively correlated with the oil filling flow rate of the friction clutch cylinder and has nothing to do with the flow diameter of the shaft-driven oil pump.

[0022] Advantages of the present invention:

[0023] The friction clutch control device driven by the branch lubricating oil boost provided by the present invention adds a working oil pump, a hydraulic motor, a first throttle valve, and a working oil safety valve compared with the traditional friction clutch control device. Among them, the combination of the hydraulic motor and the working oil pump becomes a hydraulic component of a boostable combination. Only a small amount of low-pressure lubricating oil is boosted to become the working oil, and the remaining large amount of lubricating oil does not pass through the pressure regulating valve, reducing the power loss, and thus improving the transmission efficiency of the gearbox.

[0024] When the marine gearbox applies the friction clutch control device driven by the branch lubricating oil boost of the present invention, while ensuring the normal engagement and disengagement functions of the wet friction clutch in the control gearbox, the working state of the shaft-driven oil pump in its lubrication system changes from high pressure to low pressure, the pressure loss decreases, and the decompression heat generation decreases. Therefore, the power loss consumed on the self-lubrication system of the gearbox becomes smaller, the power transmission efficiency of the gearbox is improved, and at the same time, the cooling water consumption of the self-lubrication system of the gearbox becomes lower. After the present invention makes the shaft-driven oil pump work in a low-pressure state, since the pressure resistance level of the parts of the self-lubrication system of the gearbox is reduced, the wall thickness of the oil pipeline of the lubrication system can be reduced and the weight can be lightened, that is, the power / weight ratio (power density) of the gearbox is improved, meeting the special marine applications that require strict control of the gearbox weight and gearbox efficiency. Brief Description of the Drawings

[0025] Figure 1 It is a schematic diagram of the torque transmission relationship after the traditional friction clutch control device controls the engagement of the friction clutch;

[0026] Figure 2 It is a schematic diagram of the principle during the disengagement process of the traditional friction clutch control device;

[0027] Figure 3 It is a schematic diagram of the principle after the disengagement of the traditional friction clutch control device;

[0028] Figure 4 It is a schematic diagram of the torque transmission relationship after the friction clutch of the present invention controls the engagement of the friction clutch;

[0029] Figure 5 It is a schematic diagram of the principle during the disengagement process of the present invention;

[0030] Figure 6This is the external shape interface diagram of the combination of the hydraulic motor 620 and the working oil pump 600 of the present invention;

[0031] In the above figures, P appearing in all valves represents the oil inlet of the valve, A represents the oil outlet of the valve, T represents the oil drain port of the valve, a and b respectively represent the left and right positions of the spool, DN represents the flow diameter, and the unit is millimeter;

[0032] P1 appearing in all oil pumps represents the oil outlet (high-pressure port), and T1 represents the oil suction port (low-pressure port);

[0033] P2 appearing in the hydraulic motor 620 represents the oil inlet (high-pressure port), and T2 represents the oil outlet (low-pressure port).

[0034] Reference numeral 10 is a wet friction clutch, reference numeral 20 is a traditional control device, reference numeral 40 is the control device of the present invention, reference numeral 100 is a shaft-driven oil pump, reference numeral 200 is a safety valve, reference numeral 300 is a relief valve, reference numeral 400 is a pressure regulating valve, reference numeral 500 is a connection and discharge solenoid valve, reference numeral 510 is a discharge solenoid valve, reference numeral 540 is a switching solenoid valve, reference numeral 700 is a working oil safety valve, reference numeral 600 is a working oil pump, reference numeral 610 is a connecting screw, reference numeral 620 is a hydraulic motor, reference numeral 630 is a coupling, reference numeral 640 is a connecting plate, reference numeral 650 is a throttle valve, reference numeral 800 is a quick oil filling solenoid valve, reference numeral 600-1 is a pump input interface, reference numeral 600-2 is a pump output interface, reference numeral 620-1 is a motor input interface, reference numeral 620-2 is a motor output interface, reference numeral 620-3 is a motor oil drain port, reference numeral 900 is a one-way throttle valve, and reference numeral 2000 is a quick drain valve. Detailed implementation manners

[0035] Next, the technical solutions in the embodiments of the present invention will be clearly and completely described in conjunction with the accompanying drawings in the embodiments of the present invention. Obviously, the described embodiments are only a part of the embodiments of the present invention, rather than all the embodiments. All other embodiments obtained by those of ordinary skill in the art based on the embodiments of the present invention without creative efforts shall fall within the protection scope of the present invention.

[0036] It should be noted that, without conflict, the embodiments in the present invention and the features in the embodiments may be combined with each other.

[0037] Figures 1 to 3 The schematic diagram of the principle of the traditional friction clutch control device controlling the connection and disconnection process of the friction clutch 10 is given;

[0038] As Figure 1As shown, in the traditional friction clutch control device 20, the high-pressure working oil pumped out by the shaft-driven oil pump 100 becomes low-pressure lubricating oil after passing through the pressure regulating valve 400 to lubricate the gears, bearings, and clutch.

[0039] The overflow valve 300 regulates the lubricating oil pressure, and the safety valve 200 prevents the shaft-driven oil pump 100 from operating under overpressure. After the connection and discharge solenoid valve 500 is opened and the disengagement solenoid valve 510 is closed, the working oil enters the friction clutch 10 through the connection and discharge solenoid valve 500 and the quick release valve 2000, pushing the piston in the oil cylinder 10-2 of the friction clutch 10 to compress the friction plate group and the return spring, enabling the friction clutch to transmit the gear torque.

[0040] As Figure 2 shown, in the traditional friction clutch control device 20, after the connection and discharge solenoid valve 500 is closed and the disengagement solenoid valve 510 is opened, the working oil in the oil cylinder 10-2 of the friction clutch 10 is discharged through the quick release valve 2000. The piston in the oil cylinder 10-2 of the friction clutch 10 retracts under the push of the return spring, and the piston releases the friction plate group, so that the friction clutch 10 cannot transmit the gear torque.

[0041] As Figure 3 shown, in the traditional friction clutch control device 20, the piston retracts in place under the push of the return spring, the disengagement solenoid valve 510 is closed, and the piston completely releases the friction plate group. After the connection and discharge solenoid valve 500 is closed, the pressure regulating valve 400 no longer reduces the pressure, and the pressure of the working oil pumped out by the shaft-driven oil pump 100 automatically decreases. At the same time, the lubricating oil continues to lubricate the gears, bearings, and clutch.

[0042] Figures 1 to 3 The working process of the traditional friction clutch control device 20 for controlling the friction clutch 10 is described. After the wet friction clutch 10 is connected and discharged, the shaft-driven oil pump 100 has been operating in the high-pressure area. And the pressure regulating valve 400 used in the traditional control device 20 has a large flow diameter. And it needs to match the rated flow of the shaft-driven oil pump 100. When supplying oil to the oil cylinder 10-2 of the wet friction clutch 10 under this large flow diameter, after the oil cylinder 10-2 of the wet friction clutch 10 compresses the friction plate group, the required working oil volume is about 1% of the rated flow of the shaft-driven oil pump 100. Therefore, a large amount of energy is lost when the high-pressure oil with a large flow rate is reduced in pressure by the pressure regulating valve 400 to become low-pressure oil, reducing the overall transmission efficiency of the marine gearbox. Therefore, the present invention provides a friction clutch control device driven by boosting the branch lubricating oil. For specific implementation manners, see the following:

[0043] Specific implementation manner 1. See Figures 4 to 6Regarding this embodiment, the friction clutch control device driven by branch lubricating oil boost includes a shaft-driven oil pump 100, a safety valve 200, a relief valve 300, a pressure regulating valve 400, a switching solenoid valve 540, a quick oil filling solenoid valve 800, a one-way throttle valve 900, a quick drain valve 2000 and a pressure regulating valve 400; it also includes a working oil pump 600, a hydraulic motor 620, a first throttle valve 650 and a working oil safety valve 700;

[0044] The rotor shaft of the working oil pump 600 is connected to the rotor shaft of the hydraulic motor 620 through a coupling 630; the safety valve 200 is arranged at the oil outlet of the shaft-driven oil pump 100 and is used to drain the oil with excessive pressure in the corresponding oil circuit into the gearbox;

[0045] Moreover, the oil outlet of the shaft-driven oil pump 100 is simultaneously connected to the oil inlet of the hydraulic motor 620 and the oil inlet of the throttle valve 650. The oil outlet of the hydraulic motor 620 is simultaneously connected to the low-pressure oil outlet of the pressure regulating valve 400, the oil inlet of the working oil pump 600, the oil outlet of the first throttle valve 650 and the oil inlet of the quick oil filling solenoid valve 800. And the oil outlet of the first throttle valve 650 is used as the oil outlet Pu of the control device, and this oil outlet Pu is used to supply lubricating oil to the gear 10-2 in the gearbox and the bearing 10-1 of the friction clutch 10 in the gearbox;

[0046] The relief valve 300 is arranged at the oil outlet of the first throttle valve 650 and is used to drain the oil with excessive pressure in the corresponding oil circuit into the gearbox;

[0047] The working oil safety valve 700 is arranged at the oil outlet of the working oil pump 600 and is used to drain the oil with excessive pressure in the corresponding oil circuit into the gearbox;

[0048] The oil outlet of the working oil pump 600 is connected to the high-pressure oil inlet of the pressure regulating valve 400. And on the pipeline between the oil outlet of the working oil pump 600 and the oil inlet of the quick drain valve 2000, a switching solenoid valve 540 and a one-way throttle valve 900 are arranged in sequence. The control port C of the pressure regulating valve 400 is connected to the pipeline between the switching solenoid valve 540 and the one-way throttle valve 900;

[0049] The oil outlet of the quick oil filling solenoid valve 800 is connected to the pipeline between the quick drain valve 2000 and the one-way throttle valve 900. The oil outlet Pw of the quick drain valve 2000 is connected to the oil cylinder 10-2 of the friction clutch 10 in the gearbox.

[0050] During application, the flow diameter of the pressure regulating valve 400 is only positively correlated with the oil filling flow rate of the oil cylinder of the friction clutch 10 and has nothing to do with the flow diameter of the shaft-driven oil pump 100. The flow diameter of the pressure regulating valve 400 can be flexibly selected with suitable parameters according to the volume of the oil cylinder of the friction clutch 10.

[0051] The friction clutch control device described in this embodiment adds a working oil pump 600, a hydraulic motor 620, a first throttle valve 650, and a working oil safety valve 700 compared with the traditional friction clutch control device. Among them, the combination of the hydraulic motor 620 and the working oil pump 600 becomes a hydraulic component of a pressurizable combination. Only a small amount of low-pressure lubricating oil is pressurized to become working oil, and the remaining large amount of lubricating oil does not pass through the pressure regulating valve 400, reducing power loss and thus improving the transmission efficiency of the gearbox. And it reduces the flow rate through the pressure regulating valve 400, reducing the power loss on the pressure regulating valve 400. Among them, the power loss of the pressure regulating valve 400 = the flow rate of the pressure regulating valve 400 * the pressure difference on the pressure regulating valve 400.

[0052] During specific application, the shaft-driven oil pump 100 is driven to rotate by a certain rotating shaft end of the gearbox. The shaft-driven oil pump 100 consumes the input power of the gearbox, reducing the output power of the gearbox. The low-pressure lubricating oil pumped out by the shaft-driven oil pump 100 is divided into two paths. One path flows through the throttle valve 650, and the other path flows through the hydraulic motor 620, driving the hydraulic motor 620 to rotate. The oil flowing out of the hydraulic motor 620 merges with the oil flowing out of the throttle valve 650 and enters the internal lubricating oil path of the gearbox through the lubricating oil interface Pu. The throttle valve 650 controls the oil flow rate entering the internal lubricating oil path of the gearbox, adjusts the oil flow rate entering the hydraulic motor 620, and can adjust the rotational speed of the hydraulic motor 620.

[0053] After the switching solenoid valve 540 is energized, the oil pumped out by the working oil pump 600 enters the internal working oil path of the gearbox through the switching solenoid valve 540, the one-way throttle valve 900, the quick exhaust valve 2000, and the working oil interface Pw, pushing the oil cylinder 10-2 of the wet friction clutch 10 to press the piston against the friction plate group. After the piston stops moving, the pressure at the control port C of the pressure regulating valve 400 increases, and then the pressure at the inlet port P of the pressure regulating valve 400 is adjusted to increase, boosting to high-pressure working oil and maintaining it. The wet friction clutch 10 enters a stable torque transmission state after engaging. At this time, the flow rate of the working oil path only needs to be greater than the leakage of the outlet Pw, the quick exhaust valve 2000, the switching solenoid valve 540, and the control port C of the pressure regulating valve 400 to keep the working oil pressure unchanged for a long time. At this time, the working oil flow rate is generally about 1% of the output flow rate of the shaft-driven oil pump 100. Therefore, the flow rate of the hydraulic motor 620 of the working oil pump 600 can be much smaller than the flow rate of the shaft-driven oil pump 100.

[0054] Principle analysis: The large-displacement shaft-driven oil pump 100 pumps out large-flow and low-pressure lubricating oil with a pressure of PM to lubricate the gears, bearings, and clutches. One path of the lubricating oil drives the hydraulic motor 620, and the hydraulic motor 620 drives the working oil pump 600 connected by a coaxial mechanical connection. The displacement per revolution qM of the hydraulic motor 620 is K times the displacement per revolution qG of the working oil pump 600.

[0055] Input power of the working oil pump 600: WG = QG * PG / ηG = n * qG * PG / ηG; where qG represents the displacement per revolution of the working oil pump, QG represents the oil pump flow rate QG = n * qG, PG represents the pressure generated by the working oil pump 600, and ηG represents the oil pump efficiency;

[0056] Output power of the hydraulic motor 620: WM = QM * PM * ηM = n * qM * PM * ηM = n * K * qG * PM * ηM; where, QM represents the motor flow rate, ηM represents the motor efficiency, n represents the motor speed, and K represents a coefficient: the displacement per revolution qM of the hydraulic motor 620 is K times the displacement per revolution qG of the working oil pump 600;

[0057] Since the lubricating oil drives the hydraulic motor 620 and the hydraulic motor 620 are coaxial, and the power WM = WG on the shaft is equal, thus:

[0058] Output pressure of the working oil pump 600: PG = K * ηM * ηG * PM;

[0059] If K = 7, ηM = ηG = 0.9, and PM = 0.353 Mpa, then the output pressure of the working oil pump 600 is PG = 5.67 PM = 2.0 Mpa,

[0060] The output pressure PG of the working oil pump 600 can meet the torque transmission requirement of the wet friction clutch 10 for pressing the friction plates.

[0061] Assume that the power transmitted by the gearbox using the traditional friction clutch control device is WC = 2000 Kw, the flow rate of the shaft-driven oil pump 100 is: QZ = 200 L / min, and the pressure of the shaft-driven oil pump 100 is: PZ = 2.0 Mpa.

[0062] Power of the shaft-driven oil pump 100: WZ1 = QZ * PZ / 60 = 200 * 2 = 6.67 kW.

[0063] After adopting the present invention, the power of the shaft-driven oil pump 100 is: WZ2 = QZ * PM / 60 = 200 * 0.35 / 60 = 1.17 kW.

[0064] The power loss reduction is: WZ3 = WZ1 - WZ2 = 6.67 - 1.17 = 5.5 kW.

[0065] The transmission efficiency is increased by ηg = WZ3 / WC = 5.5 / 2000 = 0.27%.

[0066] Generally, the efficiency loss of the transmission gearbox is about 1.5%. After using the present invention, the efficiency loss of the gearbox decreases to 1.23% after the efficiency is increased (1.5% - 0.27% = 1.23%), and the overall transmission efficiency of the gearbox is improved.

[0067] Specifically, the housing of the working oil pump 600 and the housing of the hydraulic motor 620 are coaxially and rigidly connected through a connecting plate 640.

[0068] In specific applications, the switching solenoid valve 540 is a two-position three-way solenoid valve, and the rapid oil filling solenoid valve 800 is a two-position two-way solenoid valve.

[0069] See Figure 4 , when the electromagnetic coil of the switching solenoid valve 540 is energized, the oil outlet of the switching solenoid valve 540 is connected to its oil inlet, and at this time, the oil cylinder 10-2 of the friction clutch 10 in the gearbox is in the oil supply state; specifically, the oil pumped out from the oil outlet of the working oil pump 600 is supplied to the oil cylinder 10-2 of the friction clutch 10 in the gearbox through the switching solenoid valve 540, the one-way passage of the one-way throttle valve 900, and the oil outlet Pw of the quick release valve 2000 in sequence.

[0070] See Figure 5 , when the electromagnetic coil of the switching solenoid valve 540 is de-energized, the oil outlet of the switching solenoid valve 540 is connected to its oil drain port T, and at this time, the oil cylinder 10-2 of the friction clutch 10 in the gearbox is in the oil drain state; specifically, the oil drained from the oil cylinder 10-2 of the friction clutch 10 in the gearbox passes through the quick release valve 2000 and the throttle passage of the one-way throttle valve 900 in sequence, and then the oil is drained out to the gearbox through the oil drain port T of the switching solenoid valve 540.

[0071] When the electromagnetic coil of the rapid oil filling solenoid valve 800 is energized, the oil outlet A of the rapid oil filling solenoid valve 800 is connected to its oil inlet P.

[0072] When the electromagnetic coil of the rapid oil filling solenoid valve 800 is de-energized, the oil outlet A of the rapid oil filling solenoid valve 800 is not connected to its oil inlet P.

[0073] The pressure regulating valve 400 automatically feedback-regulates the pressure of the oil inlet P (i.e., the inlet) according to the pressure level at the control port C without manual intervention. The rapid oil filling solenoid valve 800 has a larger diameter than the switching solenoid valve 540 and the pressure regulating valve 400. In specific applications, the flow diameter of the rapid oil filling solenoid valve 800 is DN15 (i.e., 15 mm), the flow diameter of the switching solenoid valve 540 is DN6 (i.e., 6 mm), and the flow diameter of the pressure regulating valve 400 is DN10 (i.e., 10 mm). After the rapid oil filling solenoid valve 800 is energized, the one-way throttle valve 900 restricts the flow rate of the oil flowing to the oil drain port T of the switching solenoid valve 540 to ensure rapid oil filling of the oil cylinder 10-2 of the wet friction clutch 10.

[0074] The safety valve 200 is arranged at the oil outlet of the shaft-driven oil pump 100 to prevent the shaft-driven oil pump 100 from working under overpressure. The overflow valve 300 is arranged at the oil outlet of the throttle valve 650, and the overflow valve 300 restricts the oil pressure entering the lubricating oil path inside the gearbox.

[0075] Specifically, when the pressure difference between the oil inlet and the oil outlet of the quick-release valve 2000 is higher than the pressure threshold, the quick-release port of the quick-release valve 2000 automatically opens, and the oil in the oil cylinder 10-2 of the friction clutch 10 in the gearbox is drained into the gearbox.

[0076] Specifically, the pressure threshold range between the oil inlet and the oil outlet of the quick-release valve 2000 is 0.02 MPa to 0.05 MPa.

[0077] As Figure 5 shown, for the friction clutch control device driven by branch lubricating oil boost, after the switching solenoid valve 540 is de-energized, the quick-release valve 2000 is connected to the oil drain port T of the switching solenoid valve 540 via the one-way throttle valve 900 and the switching solenoid valve 540, which can cause the quick-release valve 2000 to act. The working oil in the oil cylinder 10-2 of the friction clutch 10 is drained through the quick-release valve 2000, and the piston retracts under the push of the return spring, and the piston releases the friction plate group, so that the friction clutch 10 cannot transmit the gear torque.

[0078] As Figure 6 shown, the external shape interface diagram of the combination of the hydraulic motor 620 and the working oil pump 600 of the present invention Figure 6 In it, the oil inlet 620-1, the oil outlet 620-2 and the oil drain port 620-3 of the hydraulic motor 620 all adopt pipe joint structures; the oil inlet 600-1 and the oil outlet 600-2 of the working oil pump 600 adopt pipe joint structures; and after the housing of the working oil pump 600 and the housing of the hydraulic motor 620 are coaxially and rigidly connected through the connecting plate 640, a combined hydraulic component is formed.

[0079] Figure 6 In it, the external shape interface dimensions of the working oil pump 600 and the hydraulic motor 620 are the same. The displacement per revolution qM of the hydraulic motor 620 is K times that of the displacement per revolution qG of the working oil pump 600. K can be defined as the boost ratio, and the typical value is K≥7. The working oil pump 600 and the hydraulic motor 620 are installed face to face, and the coupling 630 is located between them. The coupling 630 is connected to the rotor shafts of both the working oil pump 600 and the hydraulic motor 620 at the same time. After the rotor shafts of the working oil pump 600 and the hydraulic motor 620 are connected through the coupling 630, they rotate synchronously. The housings of the working oil pump 600 and the hydraulic motor 620 are positioned through the positioning holes of the connecting plate 640 to ensure that the rotors of the two are on the same axis, and the connecting screws 610 fix the working oil pump 600 and the hydraulic motor 620 on the connecting plate 640.

[0080] Figure 6Among them, the flow rate and pressure of the oil inlet 620-1 of the hydraulic motor 620 are QM1 and PM1 respectively, the pressure of the oil outlet 620-2 of the hydraulic motor 620 is PM2, and the flow rate and pressure of the oil outlet 600-2 of the working oil pump 600 are QG2 and PG2 respectively. After the hydraulic motor 620 and the working oil pump 600 are connected through the connection plate 640 and the coupling 630, they become a combined hydraulic component. The beneficial effect is: the output pressure of the working oil pump 600:

[0081] PG2 = K * ηM * ηG * (PM1 - PM2) + PG1 = K * ηM * ηG * (PM1 - PM2) + PM2 = k1 * PM1 - k2 * PM2,

[0082] where k1 = K * ηM * ηG, k2 = K * ηM * ηG - 1, and further simplified to PG2 = f(K, PM1, PM2), that is, after the lubricating oil is pressurized, it can be used as the working oil to drive the wet friction clutch 10 to transmit torque.

[0083] Verification test: The flow rate of the working oil pump 600 is 2 L / min, the flow rate of the hydraulic motor 620 is 18 L / min, and the flow rate of the shaft-driven oil pump 100 is 200 L / min. The inlet pressure of the hydraulic motor 620 (equal to the outlet pressure of the shaft-driven oil pump 100) is 0.56 Mpa, and the outlet pressure of the hydraulic motor 620 (equal to the lubricating oil pressure) is 0.30 Mpa.

[0084] The outlet pressure of the working oil pump 600 is PG2 = PG + PG1, so there is:

[0085] PG2 = K * ηM * ηG * (PM1 - PM2) + PG1 = 18 / 2 * 0.9 * 0.9 * (0.56 - 0.3) + 0.3 = 2.2 Mpa, which can meet the torque transmission requirement of the wet friction clutch to compress the friction plate.

[0086] At this time, the power of the shaft-driven oil pump 100 is: WZ2 = QZ * PZ / 60 = 200 * 0.56 / 60 = 1.86 kW.

[0087] If the known control device 20 is adopted, the power of the shaft-driven oil pump 100 is: WZ1 = QZ * PZ / 60 = 200 * 1.9 / 60 = 6.33 kW.

[0088] The power loss is reduced to: WZ3 = WZ1 - WZ2 = 6.33 - 1.86 = 4.47 kW.

[0089] The transmission efficiency is increased by ηg = WZ3 / WC = 4.47 / 2000 = 0.22%.

[0090] The above verifies the effectiveness of the present invention in improving the overall efficiency of the gearbox.

[0091] Although the present invention has been described herein with reference to specific embodiments, it should be understood that these embodiments are merely examples of the principles and applications of the present invention. Accordingly, it should be understood that numerous modifications may be made to the exemplary embodiments, and other arrangements may be devised, without departing from the spirit and scope of the present invention as defined by the appended claims. It should be understood that different dependent claims and the features described herein may be combined in ways different from those described in the original claims. It should also be understood that the features described in connection with separate embodiments may be used in other described embodiments.

Claims

1. A friction clutch control device driven by branch circuit lubricating oil supercharging, comprising a shaft-driven oil pump (100), a safety valve (200), a relief valve (300), a pressure regulating valve (400), a switching solenoid valve (540), a rapid oil filling solenoid valve (800), a one-way throttle valve (900), a quick exhaust valve (2000) and a pressure regulating valve (400); characterized in that, It also includes a working oil pump (600), a hydraulic motor (620), a first throttle valve (650), and a working oil safety valve (700); The rotor shaft of the working oil pump (600) is connected to the rotor shaft of the hydraulic motor (620) through a coupling (630); the safety valve (200) is arranged at the oil outlet of the shaft-driven oil pump (100) and is used to drain the oil with excessive pressure in the oil circuit to the gearbox; Moreover, the oil outlet of the shaft-driven oil pump (100) is simultaneously connected to the oil inlet of the hydraulic motor (620) and the oil inlet of the throttle valve (650). The oil outlet of the hydraulic motor (620) is simultaneously connected to the low-pressure oil outlet of the pressure regulating valve (400), the oil inlet of the working oil pump (600), the oil outlet of the first throttle valve (650), and the oil inlet of the quick filling solenoid valve (800). And the oil outlet of the first throttle valve (650) is used as the oil outlet Pu of the control device, and this oil outlet Pu is used to supply lubricating oil to the gear (10 - 2) in the gearbox and the bearing (10 - 1) of the friction clutch (10) in the gearbox; The overflow valve (300) is arranged at the oil outlet of the first throttle valve (650) and is used to drain the oil with excessive pressure in its oil circuit to the gearbox; The working oil safety valve (700) is arranged at the oil outlet of the working oil pump (600) and is used to drain the oil with excessive pressure in its oil circuit to the gearbox; The oil outlet of the working oil pump (600) is connected to the high-pressure oil inlet of the pressure regulating valve (400). And on the pipeline between the oil outlet of the working oil pump (600) and the oil inlet of the quick release valve (2000), a switching solenoid valve (540) and a one-way throttle valve (900) are successively arranged. The control port C of the pressure regulating valve (400) is connected to the pipeline between the switching solenoid valve (540) and the one-way throttle valve (900); The oil outlet of the quick filling solenoid valve (800) is connected to the pipeline between the quick release valve (2000) and the one-way throttle valve (900), and the oil outlet Pw of the quick release valve (2000) is connected to the oil cylinder (10 - 2) of the friction clutch (10) in the gearbox.

2. The friction clutch control device driven by branch lubricating oil supercharging according to claim 1, characterized in that The oil inlet (620 - 1), oil outlet (620 - 2), and oil drain port (620 - 3) of the hydraulic motor (620) all adopt pipe joint structures; The oil inlet (600 - 1) and oil outlet (600 - 2) of the working oil pump (600) adopt pipe joint structures; And after the housing of the working oil pump (600) and the housing of the hydraulic motor (620) are coaxially and rigidly connected through a connecting plate (640), a combined hydraulic component is formed.

3. The friction clutch control device driven by the branch lubricating oil supercharger according to claim 1, wherein The switching solenoid valve (540) is a two-position three-way solenoid valve; When the electromagnetic coil of the switching solenoid valve (540) is energized, the oil outlet of the switching solenoid valve (540) is connected to its oil inlet. At this time, the oil cylinder (10 - 2) of the friction clutch (10) in the gearbox is in a state of oil supply; When the electromagnetic coil of the switching solenoid valve (540) is de-energized, the oil outlet of the switching solenoid valve (540) is connected to its oil drain port. At this time, the oil cylinder (10-2) of the friction clutch (10) in the gearbox is in the oil drain state.

4. The friction clutch control device driven by boosting the branch circuit lubricating oil according to claim 1, wherein The rapid oil filling solenoid valve (800) is a two-position two-way solenoid valve; When the electromagnetic coil of the rapid oil filling solenoid valve (800) is energized, the oil outlet of the rapid oil filling solenoid valve (800) is communicated with its oil inlet; When the electromagnetic coil of the rapid oil filling solenoid valve (800) is de-energized, the oil outlet of the rapid oil filling solenoid valve (800) is not communicated with its oil inlet.

5. The friction clutch control device driven by branch circuit lubricating oil supercharging according to claim 1, characterized in that, The flow diameter of the pressure regulating valve (400) is only positively correlated with the oil filling flow rate of the oil cylinder of the friction clutch (10), and has nothing to do with the flow diameter of the shaft-driven oil pump (100).

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